EP0138310B1 - Pompe à anneau liquide avec élément d'orifice conique ou cylindrique - Google Patents

Pompe à anneau liquide avec élément d'orifice conique ou cylindrique Download PDF

Info

Publication number
EP0138310B1
EP0138310B1 EP84305166A EP84305166A EP0138310B1 EP 0138310 B1 EP0138310 B1 EP 0138310B1 EP 84305166 A EP84305166 A EP 84305166A EP 84305166 A EP84305166 A EP 84305166A EP 0138310 B1 EP0138310 B1 EP 0138310B1
Authority
EP
European Patent Office
Prior art keywords
port
pump
conduit
vent
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84305166A
Other languages
German (de)
English (en)
Other versions
EP0138310A1 (fr
Inventor
Douglas E. Bissell
Charles M. Jozepaitis
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nash Engineering Co
Original Assignee
Nash Engineering Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nash Engineering Co filed Critical Nash Engineering Co
Publication of EP0138310A1 publication Critical patent/EP0138310A1/fr
Application granted granted Critical
Publication of EP0138310B1 publication Critical patent/EP0138310B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F04C19/005—Details concerning the admission or discharge
    • F04C19/008—Port members in the form of conical or cylindrical pieces situated in the centre of the impeller

Definitions

  • a liquid ring pump having conical port members is shown in Jennings U.S. patent 3,154,240.
  • the principal components of this pump are (1) a cylindrical housing; (2) a rotatable shaft mounted eccentrically in the housing; (3) a bladed rotor fixedly mounted on the shaft; (4) two frusto-conical port members coaxial with the shaft, each port member extending into an annular recess in a respective one of the opposite ends of the rotor and having (a) an intake port for admitting to the rotor the gas, vapor, or gas-vapor mixture to be pumped (hereinafter referred to generically as gas) and (b) a discharge port for conveying compressed gas from the rotor; and (5) a head member at each end of the pump for conveying gas between the associated port member and appropriate pump inlets and outlets.
  • a quantity of pumping liquid e.g., water
  • the rotor blades engage the pumping liquid and form it into an annular ring concentric with the housing.
  • the liquid ring cooperates with the rotor blades to form a plurality of gas pumping chambers, each chamber being bounded by (1) two adjacent rotor blades, (2) the adjacent portion of the rotor hub or the conical port member, and (3) the adjacent portion of the inner surface of the liquid ring. Because the rotor is eccentric to the housing, these pumping chambers vary in size in a cyclic fashion as the rotor rotates.
  • the pumping chambers are expanding. This is the gas intake zone of the pump, and the intake ports are therefore located so as to communicate with the pumping chambers in this zone.
  • the pumping chambers are contracting. This is the gas compression zone of the pump, and the discharge ports are therefore located so as to communicate with the pumping chambers in this zone.
  • liquid ring pumps Another consideration in the design of liquid ring pumps is that the higher the compression ratio the pump is designed to achieve, the more sensitive the pump becomes to off-normal operating conditions. Typically, if a liquid ring pump is designed to achieve a very high compression ratio, it is subject to very severe overcompression problems at lower than normal compression ratios. Similarly, unless a liquid ring pump is designed to achieve a high compression ratio (in which case it typically operates less efficiently at lower compression ratios), it generally cannot achieve such high compression ratios at all.
  • liquid ring pumps especially those designed for operation at relatively low speeds and low compression ratios, is that such pumps may exhibit instability manifested by excessive vibration and loss of pumping ability when subjected to compression ratios higher than the design compression ratio. This condition may be ameliorated by increasing the flow of pumping liquid to the pump. But this approach usually increases pump operating cost and may only shift the point at which the pump becomes unstable.
  • the vent-recirculation port acts as a vent or an additional discharge port for allowing gas to reach the pump outlet via the sump chamber. This substantially prevents overcompression of the gas at low compression ratios.
  • the vent-recirculation port may be essentially inoperative, being substantially closed off by the pumping liquid in the sump chamber.
  • pumping liquid from the sump chamber is pulled back into the liquid ring via the vent-recirculation port, which then acts as a recirculation path.
  • illustrative liquid ring pump 10 includes cylindrical housing 12 having two head members 14a and 14b at respective opposite ends of housing 12. Because the two ends of the pump are substantially mirror images of one another, only the left-hand end of the pump as viewed in Figure 1 will be shown and described in full detail herein.
  • Each head 14a, 14b has a pump inlet 16a, 16b, respectively.
  • Each head 14a, 14b also has a primary pump outlet 18a, 18b, respectively, and an alternate pump outlet 18x, 18y, respectively.
  • either outlet can be used in each head to suit the convenience of the user.
  • the outlet which is not being used is covered by a cover plate.
  • Gas to be pumped is supplied to inlets 16 via conduits (not shown). After compression by the pump, the gas exits via outlets 18 and is conveyed away by other conduits (also not shown).
  • Shaft 20 is eccentrically mounted for rotation in housing 12. In other words, the rotational axis of shaft 20 is parallel to but laterally offset from the central axis of cylindrical housing 12. Shaft 20 passes through each head 14 and is supported for rotation by bearing assemblies 22 fixed to the heads. Shaft 20 is rotated by a suitable pump motor (not shown) in the direction indicated by arrow 50.
  • a rotor 30 Fixedly mounted on shaft 20 inside housing 12 is a rotor 30 having a plurality of blades 32 extending radially outward from hub 34.
  • the cross sectional shape of each blade and the typical circumferential spacing of the blades around the rotor hub are illustrated in Figure 15. Although hooked slightly near their outer tips, blades 32 may be thought of as substantially planar, the plane of each blade being parallel to the axis of shaft 20.
  • Blades 32 are substantially longer parallel to shaft 20 than hub 34. Blades 32 are divided in half lengthwise and also stiffened by annular divider 36, which extends radially outward from hub 34 all the way to the outer tips of the blades. Each half of each blade has three lengthwise parts: a first part 32a where the blade is connected to hub 34; a second part 32b where the blade is radially spaced from shaft 20 and unsupported by any connection to the adjacent blades; and a third part 32c where the blade is also radially spaced from shaft 20 but connected to annular end shroud 38.
  • Annular end shroud 38 is a substantially planar toroidal or washer-shaped member which extends from an inner circle immediately adjacent to port member 40 (described below) to an outer circle adjacent the outer tips of blades 32. End shroud 38 stiffens the otherwise unsupported ends of blades 32 and also closes off the ends of the gas pumping chambers formed between adjacent blades. Although only one end of rotor 30 is visible in Figure 3, it will be understood that there is an end shroud 38 at each end of the rotor.
  • each blade 32 is radially spaced from shaft 20 because the above-described second and third portions 32b and 32c of each blade 32 are radially spaced from shaft 20, the result is an annular space around shaft 20 adjacent each end of the rotor.
  • An annular port member 40 is fixedly mounted on each of head members 14 and projects into this annular space at the adjacent end of rotor 30.
  • each of port members 40 is an annular structure surrounding the adjacent portion of shaft 20.
  • each port member 40 includes an intake port 42 which is located near the inner edges of rotor blade portions 32b adjacent the intake zone of the pump. Port member 40 also defines an intake conduit 44 which connects to an intake conduit 64 in the adjacent head member 14. Intake conduit 64 leads to the associated pump inlet 16. Gas supplied to pump inlet 16 is therefore drawn into the intake zone of the pump via conduits 64 and 44 and intake port 42.
  • each port member 40 further includes a discharge port 46 which is located near the edges of rotor blade portions 32b adjacent the compression zone of the pump.
  • Port member 40 also defines a discharge conduit 48 which connects to a discharge conduit 68 in the adjacent head member 14.
  • Discharge conduit 68 leads to the associated pump outlet 18 (see Figure 4). Gas compressed by the pump is therefore discharged from the compression zone of the pump via discharge port 46 and discharge conduits 48 and 68.
  • port member 40 is better seen in Figures 10-14.
  • Figure 10 is an end view of left-hand port member 40 as seen from the adjacent head member 14a.
  • Figure 12 is an opposite end view of the same port member. Proceeding counterclockwise around the structure shown in Figure 10, intake conduit 44 occupies approximately one half of the interior of the port member. Intake port 42 spans a major portion of conduit 44.
  • vent conduit 70 which communicates with vent port 72 in the conical outer surface of the port member. The operation of vent ports 72 will be described in greater detail below, but it should be noted here that vent port 72 is located near the inner edges of rotor blade portions 32b adjacent an initial portion of the compression zone of the pump.
  • vent-recirculation conduit 74 which communicates with vent-recirculation port 76.
  • Vent-recirculation port 76 is located near the inner edges of rotor blade portions 32b adjacent an intermediate portion of the compression zone of the pump.
  • discharge port 46 and associated discharge conduit 48 The next portion of port member 40 is discharge port 46 and associated discharge conduit 48.
  • the final portion of port member 40 is pumping liquid conduit 78 for conveying pumping liquid from conduit 24 to a point adjacent the rotor hub to replenish the liquid ring and to also provide a gas seal at that point in the pump.
  • intake conduit 64 can be seen in broken lines in Figure 4 to be a relatively large semi-cylindrical chamber which communicates with pump inlet 16a at the top of the pump (see also Figures 3 and 8).
  • Vent conduit 80 is also visible in broken lines in Figure 4 as a truncated wedge shaped chamber which leads to check valve assembly 90 (see also Figures 7 and 9).
  • Check valve assembly 90 includes ball-type check valve 92 between vent conduit 80 and vent-recirculation conduit 84. When the pressure in vent conduit 80 is greater than the pressure in vent-recirculation conduit 84, check valve 92 opens to allow fluid to flow from conduit 80 to conduit 84.
  • Check valve assembly 90 has a removable cover plate 94 for facilitating maintenance of check valve 92.
  • the check valve ball is guided by three parallel pins 96 (only two of which are visible in Figure 9) which are mounted on cover plate 94 and which slope downwardly away from the cover plate toward the wall between conduits 80 and 84.
  • One or more additional horizontal pins 98 are mounted on the wall between conduits 80 and 84 to temporarily support the check valve ball during removal or replacement of cover plate 94.
  • Vent-recirculation conduit 84 is also visible in broken lines in Figure 4.
  • the portion of conduit 84 closest to port member 40 is another truncated wedge shaped chamber which communicates with the lower portion of check valve assembly 90 (see also Figure 9).
  • vent-recirculation conduit 84 runs vertically downward and has an approximately square cross section as can be seen in Figure 5 (see also Figure 9).
  • vent-recirculation conduit 84 makes a right angle turn and runs horizontally across the pump (see Figures 4, 5, and 8).
  • vent-recirculation conduit 84 opens out into the bottom of a sump chamber 100 formed in head member 14 to the right of baffle member 102.
  • Discharge conduit 68 is visible in both dotted and solid lines in Figure 4. The portion of conduit 68 to the right of baffle member 102 as viewed in Figure 4 communicates with sump chamber 100 as mentioned above. To the left of baffle member 102, conduit 68 communicates with pump outlet 18a and alternate pump outlet 18x.
  • Pumping liquid conduit 88 is also visible in broken lines in Figure 4 and is another truncated wedge shaped chamber which communicates with pumping liquid supply conduit 24.
  • vent-recirculation port 76 and the associated conduits therefore further relieve the early build-up of gas pressure in the compression zone of the pump at low compression ratios.
  • the final portion of the gas in rotor 30 again reaches the final discharge pressure of the pump adjacent discharge pump 46. Accordingly, the final portion of the gas (and some pumping liquid) exits from the rotor via discharge port 46. This fluid flows through conduits 48 and 68 and exits from the via pump outlet 18.
  • the gas does not reach the final discharge pressure of the pump until after passing vent port 72. Accordingly, the gas pressure in conduit 80 is less than the pressure in conduit 84 and check valve 92 is closed. Vent port 72 is therefore effectively closed. The gas does reach the final discharge pressure of the pump adjacent vent-recirculation port 76. Accordingly, a portion of the gas exits from rotor 30 via vent-recirculation port 76. This gas flows through conduits 74 and 84, through sump chamber 100, and into conduit 68, which conveys it to pump outlet 18. Vent-recirculation port 76 and the associated conduits therefore act as a vent for relieving early build-up of gas pressure in the pump when operating at intermediate compression ratios.
  • this invention greatly extends the range of compression ratios over which a conically or cylindrically ported liquid ring pump can be made to operate efficiently.
  • the vent port 72 and/or vent-recirculation port 76 prevent wasteful overcompression of the gas in the rotor of the pump, thereby reducing the power required to operate the pump at these compression ratios.
  • vent port 72 is closed and vent-recirculation port 76 is also either effectively closed or recirculating fluid including a high proportion of pump liquid, thereby extending the operating range of the pump to compression ratios substantially higher than could otherwise be attained.
  • the present invention also enables conically or cylindrically ported liquid ring pumps to better respond to operating condition fluctuations. For example, if the flow of gas to the pump suddenly increases, or if a large slug of liquid suddenly enters the pump via pump inlet 16, vent port 72 and/or vent-recirculation port 76 instantly and automatically begin to vent rotor 30 to prevent overcompression in the pump.
  • vent port 72 and associated conduits 70 and 80 and check valve assembly 90 can be eliminated as shown in Figure 16.
  • the pump of Figure 16 can be the same as shown and described above, except that it will not have the early venting provided by vent port 72 and the associated elements.
  • Vent-recirculation port 76 can be provided with a nozzle shape as shown in Figure 17.
  • This nozzle shape is smoothly convergent in the favorable or inward flow direction and is square-edged in the unfavorable or outward flow direction. This shape promotes inward flow (i.e., venting), and somewhat inhibits outward flow (i.e., recirculation). This may be desirable so that port 76, which is of fixed size, provides a larger volume of venting flow than recirculation flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Closures For Containers (AREA)
  • Reciprocating Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (4)

1. Pompe à anneau liquide (10) comprenant:
-une enveloppe annulaire longitudinale (12);
-un arbre rotatif (20) présentant un axe longitudinal parallèle à l'axe longitudinal de l'enveloppe, l'arbre étant monté excentriquement dans l'enveloppe;
-un rotor (30) monté solidaire sur l'arbre (20) et comportant une série de pales (32) s'étendant radialement vers l'extérieur à partir de l'arbre dans des plans sensiblement parallèles à l'axe longitudinal de l'arbre, chaque pale présentant une première (32a), une seconde (32b) et une troisième (32c) parties adjacentes l'une de l'autre suivant la longueur de l'arbre, chaque pale étant reliée à l'arbre près de la première partie et étant radialement espacée de l'arbre près des seconde et troisième parties, et un anneau de renforcement toroidal planaire (38) disposé autour de l'arbre et radialement espacé de lui, l'anneau de renforcement toroïdal reliant les troisièmes parties de toutes les pales;
-un organe d'ajutage annulaire (40) disposé autour de l'arbre (12) et pénétrant dans l'espace annulaire séparant l'arbre (12) et les secondes (32b) et troisièmes (32c) parties des pales, l'organe d'ajutage définissant un premier et un second orifices (42, 46) près des secondes parties des pales, le premier orifice (42) étant un ajutage d'admission pour l'introduction de gaz dans le rotor dans une zone d'admission de la pompe, le second orifice (46) étant un ajutage de sortie pour la réception de gaz sortant du rotor dans une zone de compression de la pompe, et
-un organe de tête (14a; 14b) relié à l'organe d'ajutage (40) à distance du rotor et définissant une entrée de pompe (16a; 16b) pour l'admission de gaz à pomper et une sortie. de pompe (18a; 18b; 18x; 18y) pour la sortie de gaz pompé par la pompe, l'organe d'ajutage (40) et l'organe de tête (14a, 14b) définissant en outre conjointement un premier conduit (44, 64) entre l'entrée de la pompe et l'ajutage d'admission et un second conduit (48, 68) entre l'ajutage de sortie et la sortie de la pompe,

caractérisée en ce que l'organe d'ajutage annulaire (40) définit voisin des secondes parties des pales encore un troisième orifice (76) comportant un ajutage d'évent-recyclage situé après l'ajutage d'admission (42), mais avant l'ajutage de sortie (46) dans le sens de rotation du rotor (50); l'organe de tête (14a, 14b) définit encore une chambre de carter (100) pour retenir normalement une certaine quantité de liquide de pompage dans la tête, et en ce que l'organe d'ajutage (40) et l'organe de tête (14a; 14b) ensemble définissent encore un troisième conduit (74, 84) entre l'ajutage d'évent-recyclage (76) et un emplacement situé dans la chambre de puisard (100) au-dessous du niveau normal atteint par le liquide de pompage dans la chambre de carter, le second conduit (48, 68) communiquant aussi avec la chambre de carter (100) mais en un point situé au-dessus du niveau normal atteint par le liquide de pompage dans la chambre de carter.
2. Appareil selon la revendication 1, caractérisé en ce que l'organe d'ajutage (40) présente encore un quatrième orifice (72) voisin des secondes parties (32b) des pales (32), le quatrième orifice étant un ajutage d'évent situé après l'ajutage d'admission (42) mais avant l'ajutage d'évent- recyclage (76) dans le sens de rotation du rotor (50), et en ce que l'organe d'ajutage (40) et l'organe de tête (14a; 14b) définissent encore conjointement un quatrième conduit (70, 80) entre l'ajutage d'évent (72) et le troisième conduit (84), une soupape de retenue (92) étant disposée dans le quatrième conduit (80) pour ne permettre l'écoulement de fluide que depuis l'ajutage d'évent (72) vers le troisième conduit (84).
3. Appareil selon la revendication 1, caractérisé en ce que l'ajutage d'évent-recyclage (76) a une forme de buse pour favoriser l'écoulement vers l'intérieur de l'organe d'ajutage (40) à partir du rotor (30) et pour réfréner l'écoulement dans le sens opposé.
4. Appareil selon la revendication 1, caractérisé en ce que l'ajutage d'évent-recyclage est incliné dans les sens de mouvement (50) de la partie voisine du rotor.
EP84305166A 1983-08-08 1984-07-30 Pompe à anneau liquide avec élément d'orifice conique ou cylindrique Expired EP0138310B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/521,449 US4498844A (en) 1983-08-08 1983-08-08 Liquid ring pump with conical or cylindrical port member
US521449 1983-08-08

Publications (2)

Publication Number Publication Date
EP0138310A1 EP0138310A1 (fr) 1985-04-24
EP0138310B1 true EP0138310B1 (fr) 1987-11-04

Family

ID=24076778

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84305166A Expired EP0138310B1 (fr) 1983-08-08 1984-07-30 Pompe à anneau liquide avec élément d'orifice conique ou cylindrique

Country Status (10)

Country Link
US (1) US4498844A (fr)
EP (1) EP0138310B1 (fr)
JP (1) JPS6060292A (fr)
AU (1) AU562164B2 (fr)
BR (1) BR8403947A (fr)
CA (1) CA1233148A (fr)
DE (1) DE3429085C2 (fr)
FI (1) FI76628C (fr)
SE (1) SE456028B (fr)
ZA (1) ZA845797B (fr)

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4747752A (en) * 1987-04-20 1988-05-31 Somarakis, Inc. Sealing and dynamic operation of a liquid ring pump
FI882712A (fi) * 1988-06-08 1989-12-09 Pentamo Oy Vaetskeringkompressor.
US4914921A (en) * 1988-08-16 1990-04-10 Cbi Research Corporation Refrigeration method and apparatus using aqueous liquid sealed compressor
ATE82620T1 (de) * 1989-06-05 1992-12-15 Siemens Ag Fluessigkeitsringverdichter.
US5100300A (en) * 1990-12-28 1992-03-31 The Nash Engineering Company Liquid ring pumps having rotating lobe liners with end walls
US5246348A (en) * 1992-05-14 1993-09-21 Vooner Vacuum Pumps, Inc. Liquid ring vacuum pump-compressor with double function of liquid ring with separate sources
US5356268A (en) * 1993-09-29 1994-10-18 The Nash Engineering Company Check valve structures for liquid ring pumps
DE9406597U1 (de) * 1994-04-20 1995-08-24 Sihi GmbH & Co KG, 25524 Itzehoe Flüssigkeitsringgaspumpe
CN1071004C (zh) * 1995-08-21 2001-09-12 西门子公司 环形液体压缩机
US5961295A (en) * 1997-07-03 1999-10-05 The Nash Engineering Company Mixed flow liquid ring pumps
DE19847681C1 (de) * 1998-10-15 2000-06-15 Siemens Ag Flüssigkeitsringpumpe
US6692234B2 (en) * 1999-03-22 2004-02-17 Water Management Systems Pump system with vacuum source
US6390768B1 (en) 1999-03-22 2002-05-21 David Muhs Pump impeller and related components
US6405748B1 (en) * 1999-03-22 2002-06-18 David Muhs Trailer and fuel tank assembly
US6315524B1 (en) 1999-03-22 2001-11-13 David Muhs Pump system with vacuum source
US20080175722A1 (en) * 2007-01-19 2008-07-24 David Muhs Vacuum pump with wear adjustment
US7878768B2 (en) * 2007-01-19 2011-02-01 David Muhs Vacuum pump with wear adjustment
CA2766385C (fr) 2009-06-26 2016-10-18 Gardner Denver Nash, Llc Procede de conversion de pompes a anneau liquide comprenant des events pour liquide d'etancheite
US8998586B2 (en) * 2009-08-24 2015-04-07 David Muhs Self priming pump assembly with a direct drive vacuum pump
US20110194950A1 (en) * 2010-02-10 2011-08-11 Shenoi Ramesh B Efficiency improvements for liquid ring pumps
FI126831B (fi) * 2010-04-14 2017-06-15 Evac Oy Nesterengaspumppu ja menetelmä nesterengaspumpun käyttämiseksi
US8662118B2 (en) 2011-12-01 2014-03-04 Emco Wheaton Corp. Liquid filling system
US20150176581A1 (en) * 2012-07-09 2015-06-25 Jets As Liquid ring screw pump design
US9541086B2 (en) * 2013-10-01 2017-01-10 Gardner Denver Nash Llc Liquid ring pump with modular construction, an inter-stage bypass and overload protection
JP2018501429A (ja) * 2015-01-08 2018-01-18 ガードナー デンヴァー ナッシュ エルエルシーＧａｒｄｎｅｒ Ｄｅｎｖｅｒ Ｎａｓｈ Ｌｌｃ コンプレッサ型液封式ポンプにおける低圧封液入口領域
CA2975876A1 (fr) * 2015-02-12 2016-08-18 Gardner Denver Nash Llc Element formant orifice de pompe a anneau liquide ayant des constructions anti-cavitation
CN105485030A (zh) * 2015-12-29 2016-04-13 扬州长江水泵有限公司 一种单级锥体真空泵
KR101803843B1 (ko) * 2017-08-24 2017-12-04 주식회사 백콤 내부 부품 교체가 용이한 수봉식 진공펌프
GB2571969B (en) * 2018-03-14 2020-10-07 Edwards Tech Vacuum Engineering Qingdao Co Ltd A liquid ring pump manifold with an integrated spray nozzle
GB2571970B (en) * 2018-03-14 2020-09-16 Edwards Tech Vacuum Engineering (Qingdao) Co Ltd A liquid ring pump manifold with integrated non-return valve

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE274015C (fr) *
GB190611378A (en) * 1906-05-15 1907-02-21 James Osborn Spong Improved Appliance for Securing Flexible Hose Piping to Plugs, Taps, Sprinklers, Connections or the like.
US1180613A (en) * 1913-03-19 1916-04-25 Siemens Schuckertwerke Gmbh Rotary pump.
US2211316A (en) * 1936-02-21 1940-08-13 Bingham Pump Company Inc Wet type gas pump
CH206273A (de) * 1938-04-28 1939-07-31 Sulzer Ag Pumpe mit durch einen Flüssigkeitsring abgedichtetem Zellenlaufrad.
US2344396A (en) * 1940-01-22 1944-03-14 Dardelet Robert Leon Compression or depression pump of the liquid ring type
US2453373A (en) * 1944-08-28 1948-11-09 Kollsman Paul Compressor
US3043498A (en) * 1959-12-29 1962-07-10 Gabbioneta Roberto Rotary liquid ring pump with means for regulating the loading of liquid in the ring
US3154240A (en) * 1961-02-20 1964-10-27 Nash Engineering Co Pumping device
DE1294819B (de) * 1964-03-25 1969-05-08 Siemens Ag Verfahren zum Drosseln oder Verhindern des Stroemens eines Mediums durch eine Wandoeffnung von einem Raum hoeheren Druckes in einen Raum niederen Druckes und Anwendung des Verfahrens
US3217975A (en) * 1964-12-17 1965-11-16 Nash Engineering Co Pump device
DE1503605B2 (de) * 1965-04-28 1971-05-27 Siemens AG, 1000 Berlin u 8000 München Rueckschlagventil fuer eine fluessigkeitsringgaspumpe
AT282798B (de) * 1967-06-09 1970-07-10 Irving C Jennings Mehrstufige Flüssigkeitsring-Rotationspumpe
GB1284473A (en) * 1969-04-26 1972-08-09 Siemens Ag Improvements in or relating to liquid ring pumps
US3588283A (en) * 1969-10-27 1971-06-28 Nash Engineering Co Vacuum pump or compressor
US3707337A (en) * 1971-02-23 1972-12-26 Siemen & Hinsch Gmbh Liquid seal compressors
DE2318538B2 (de) * 1973-04-12 1975-12-04 Siemens Ag, 1000 Berlin Und 8000 Muenchen Verteiler für einen Flüssigkeitsringgasverdichter
DE2704863A1 (de) * 1977-02-05 1978-08-10 Kloeckner Humboldt Deutz Ag Rueckschlagventil fuer eine fluessigkeitsring-gaspumpe
JPS555427A (en) * 1978-06-22 1980-01-16 Nakamura Suikan:Kk Water ring pump of internal-air-port type
US4254305A (en) * 1979-02-07 1981-03-03 International Telephone And Telegraph Corporation Current limited subscriber line feed circuit
GB2064002A (en) * 1979-11-22 1981-06-10 Graham Precision Pumps Ltd Liquid Ring Vacuum Pumps
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control

Also Published As

Publication number Publication date
DE3429085C2 (de) 1995-11-23
AU562164B2 (en) 1987-05-28
CA1233148A (fr) 1988-02-23
DE3429085A1 (de) 1985-02-28
FI843121A (fi) 1985-02-09
FI843121A0 (fi) 1984-08-08
ZA845797B (en) 1985-03-27
BR8403947A (pt) 1985-07-09
SE8403918L (sv) 1985-02-09
SE8403918D0 (sv) 1984-07-31
EP0138310A1 (fr) 1985-04-24
US4498844A (en) 1985-02-12
JPH0438918B2 (fr) 1992-06-25
SE456028B (sv) 1988-08-29
FI76628B (fi) 1988-07-29
FI76628C (fi) 1988-11-10
AU3111984A (en) 1985-02-14
JPS6060292A (ja) 1985-04-06

Similar Documents

Publication Publication Date Title
EP0138310B1 (fr) Pompe à anneau liquide avec élément d'orifice conique ou cylindrique
EP0155419B1 (fr) Réglage de bruit pour pompes à anneau liquide avec passages placés en cône
EP0515633B1 (fr) Pompe a auto-amorcage
US2832292A (en) Pump assemblies
US5100289A (en) Self-priming centrifugal pump
US5078573A (en) Liquid ring pump having tapered blades and housing
US4545730A (en) Liquid ring vacuum pump for gaseous media
US3108738A (en) Liquid-ring gas pumps
US3944406A (en) Centrifugal pump for pumping liquids with heavy gas content
US4551070A (en) Noise control for conically ported liquid ring pumps
US4978276A (en) Pump stage for a high-vacuum pump
US4392783A (en) Liquid ring pump employing discharged pumping liquid for discharge port control
US5116198A (en) Centrifugal pumping apparatus
US3228344A (en) Centrifugal impeller and method of making same
EP0420886B1 (fr) Compresseur a anneau liquide
EP0274272A2 (fr) Pompe à anneau liquide à deux étages
EP0856664B1 (fr) Pompes à anneau liquide à deux étages
US4815930A (en) Cavitating centrifugal pump
US4153385A (en) Self-drawing centrifugal pump
US3351272A (en) Vacuum pump
US4401409A (en) Self-priming centrifugal pump
EP1274943A2 (fr) Pompe a combustible pour turbines a gaz
US3227089A (en) Centrifugal pump
US3090321A (en) Vapor separating pump
US3491697A (en) Hydraulic fuel oil pump or the like

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): BE FR GB IT

17P Request for examination filed

Effective date: 19851002

17Q First examination report despatched

Effective date: 19860901

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE FR GB IT

ITF It: translation for a ep patent filed
ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19940620

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19950731

BERE Be: lapsed

Owner name: THE NASH ENGINEERING CY

Effective date: 19950731

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20010611

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20010615

Year of fee payment: 18

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020730

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20020730

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030331

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP